DE102024106815A1 - Bearing arrangement of a shaft on a component, in particular of a motor vehicle, electrical machine for a motor vehicle and motor vehicle - Google Patents

Abstract

The invention relates to a bearing arrangement (9) of a shaft (7) on a component (8) that is formed separately from the shaft (7) and provided in addition to the shaft (7), in which the shaft (7) is mounted on the component (8) via at least one rolling bearing (10) so as to be rotatable about an axis of rotation (4) relative to the component (8). A channel (16) is provided that runs at least partially in the shaft (7) and through which a coolant and/or lubricant can flow, which channel has an outlet opening (17) through which the coolant and/or lubricant can flow and via which the coolant and/or lubricant can be discharged from the channel (16) in order to thereby supply the at least one cooling and/or lubrication point (S) with the coolant and/or lubricant.

Description

The invention relates to a bearing arrangement for a shaft on a component, in particular of a motor vehicle, according to the preamble of patent claim 1. Furthermore, the invention relates to an electric machine for a motor vehicle, comprising at least one such bearing arrangement. The invention also relates to a motor vehicle comprising at least one such electric machine.

The DE 10 2020 101 951 A1 discloses a rolling bearing having an inner ring and an outer ring arranged radially outwardly of the inner ring to face the inner ring. A plurality of rolling elements are also provided, which are arranged between the inner ring and the outer ring. The rolling bearing also has a cage that holds a plurality of the rolling elements.

The object of the present invention is to provide a bearing arrangement of a shaft on a component, in particular of a motor vehicle, an electrical machine with at least one such bearing arrangement and a motor vehicle with at least one such electrical machine, so that a particularly advantageous supply of at least one point with a coolant and/or lubricant can be realized.

This object is achieved according to the invention by a bearing arrangement having the features of patent claim 1, by an electric machine having the features of patent claim 6, and by a motor vehicle having the features of patent claim 10. Advantageous embodiments of the invention are the subject of the dependent claims.

A first aspect of the invention relates to a bearing arrangement for a shaft on a component, in particular a motor vehicle, which is formed separately from the shaft and provided in addition to the shaft. This means, for example, that the motor vehicle, also simply referred to as a vehicle and preferably designed as a motor vehicle, in particular as a passenger car, in its fully manufactured state has the bearing arrangement and thus the shaft and the component formed separately from the shaft and provided in addition to the shaft. In the bearing arrangement, the shaft is rotatably mounted on the component about an axis of rotation relative to the component via at least one rolling bearing, which is formed in particular separately from the shaft and separately from the component and very particularly provided in addition to the shaft and in addition to the component. The rolling bearing has rolling elements formed separately from the shaft and separately from the component, which can be designed, for example, as balls. If the shaft rotates about the axis of rotation relative to the component, the rolling elements roll, in particular directly, on an inner, first raceway and on an outer, second raceway, wherein the outer raceway is arranged further outward in the radial direction of the shaft than the inner raceway. In particular, the raceways face one another in the radial direction of the shaft. The rolling bearing also has a cage formed separately from the shaft and separately from the component and also separately from the rolling elements, by means of which the rolling elements are held at a respective distance from one another running in the circumferential direction of the shaft. The circumferential direction of the shaft runs around the axis of rotation, so that in particular the circumferential direction of the shaft runs in a plane that is perpendicular to the axial direction of the shaft, the radial direction of which is perpendicular to the axial direction of the shaft. Thus, for example, the radial direction of the shaft also runs in the aforementioned plane. The axial direction of the shaft coincides with the axis of rotation.

The bearing arrangement includes a channel extending at least partially within the shaft through which a coolant and/or lubricant can flow. Preferably, the coolant and/or lubricant is a component of the bearing arrangement. The coolant and/or lubricant is also referred to as a fluid. Thus, when reference is made to the fluid above and below, this refers to the coolant and/or lubricant, unless otherwise stated. Preferably, the fluid is liquid. Most preferably, the fluid is an oil. Since the channel extends at least partially within the shaft, i.e., inside the shaft, at least part of the channel extends within the shaft, i.e., inside the shaft, so that, for example, part of the channel can be delimited, in particular directly, by an inner circumferential surface of the shaft. If the fluid thus flows through the shaft, i.e., through part of the channel, the fluid directly contacts, for example, the inner circumferential surface. In particular during operation of a device having the bearing arrangement, in particular of the motor vehicle, the fluid flows in a flow direction through the channel, which is also referred to as an oil channel, in particular when the fluid is an oil.

The channel has, in particular, an outlet opening through which the fluid can flow, through which the fluid can be discharged from the channel in order to supply at least one cooling and/or lubricating point, also referred to simply as a point, with the cooling and/or lubricating agent. This location is, for example, a location at which, when the shaft rotates about the axis of rotation relative to the component, at least two elements slide against one another, in particular directly. The first of the elements can be the shaft, and a second of the elements can be, for example, a sealing element, such as a radial shaft seal, so that, for example, when the shaft rotates about the axis of rotation relative to the component, the sealing element slides, in particular directly, against an outer circumferential surface of the shaft. The sealing element is, for example, formed separately from the component and separately from the shaft, wherein, for example, the sealing element can be fastened at least indirectly, in particular directly, to the component, in particular in such a way that relative rotations between the sealing element and the component, at least around the axis of rotation, are prevented. Thus, in particular, the shaft is rotatable about the axis of rotation relative to the sealing element.

The outlet opening is at least partially, in particular at least predominantly and thus at least more than half or completely, overlapped outwardly in the radial direction of the shaft by the cage of the rolling bearing, which is rotatable about the rotational axis relative to the outlet opening and relative to the shaft. In particular, the cage is rotatable about the rotational axis relative to the component.

In order to be able to supply the coolant and/or lubricant with the fluid in a particularly advantageous manner, the invention provides that the cage has at least two sub-regions which, in particular, directly follow one another in the circumferential direction of the cage running around the axis of rotation and thus each extend in the circumferential direction of the cage, the circumferential direction of which coincides with the circumferential direction of the shaft, namely a first sub-region and a second sub-region. In at least one first rotational position of the cage, the outlet opening is at least partially, in particular at least predominantly and thus at least more than half or completely, overlapped towards the outside in the radial direction of the shaft by the first sub-region. In at least one second rotational position of the cage which is different from the first rotational position, the outlet opening is at least partially, in particular at least predominantly and thus at least more than half or completely, overlapped towards the outside in the radial direction of the shaft by the second sub-region. In particular, it is provided that in the first rotational position the outlet opening is arranged without overlapping with the second partial region as viewed outwards in the radial direction of the shaft, so that it is preferably provided that in the first rotational position of the cage the outlet opening is not overlapped by the second partial region as viewed outwards in the radial direction of the shaft. Furthermore, it is preferably provided that in the second rotational position the outlet opening is arranged without overlapping with the first partial region as viewed outwards in the radial direction of the shaft, so that preferably in the second rotational position the outlet opening is not overlapped by the first partial region as viewed outwards in the radial direction of the shaft.

Furthermore, the invention provides that the second sub-region opens the outlet opening to a greater extent than the first sub-region, which blocks the outlet opening to a greater extent than the second sub-region. This means that when the cage is in the second rotational position relative to the outlet opening, the second sub-region opens the outlet opening to a greater extent outwards in the radial direction of the shaft than when the cage is in the first rotational position relative to the outlet opening, so that when the cage is in the first rotational position relative to the outlet opening, the cage fluidically blocks the outlet opening to a greater extent outwards in the radial direction of the shaft than when the cage is in the second rotational position relative to the outlet opening. In other words, again in the first rotational position of the cage, the first sub-region throttles the outlet opening to a greater extent outwards in the radial direction of the shaft than the second sub-region in the second rotational position of the cage. Conversely, in the second rotational position of the cage, the second section of the cage throttles the outlet opening less strongly, viewed outward in the radial direction of the shaft, than the first section of the cage in the first rotational position of the cage. This makes it particularly easy to ensure a sufficient supply of fluid to the location, in particular in such a way that both an insufficient supply of fluid to the location and an oversupply of fluid to the location can be avoided. The invention is based in particular on the following findings and considerations:

It is known from reciprocating piston machines, also referred to as piston-operated machines, especially those of motor vehicles, that, for example, friction and/or sliding partners should be supplied with a coolant and/or lubricant in order to supply the friction and/or sliding partners, also referred to simply as partners, with a sufficient quantity of the coolant and/or lubricant. If the coolant and/or lubricant is in the form of an oil, the supply of the partners with the coolant and/or lubricant is also referred to as oiling or lubrication. For this purpose, a circuit is usually used. A flow concept has been developed that takes the needs of the partners into account and can ensure that a necessary and advantageous amount of the coolant and/or lubricant, preferably in liquid form, is delivered to the partners and thus to at least one point for a given operating condition. In particular, the fluid is used to avoid excessive friction at that point and/or to dissipate heat and thus avoid excessively high temperatures. In contrast to such reciprocating piston machines, electric machines, which are used, for example, as electric drive motors for the, in particular, purely electric, propulsion of motor vehicles, do not have any oscillating components due to their design. While in reciprocating piston machines, for example, friction and/or sliding and/or lubricating partners can simply be supplied with the fluid by means of a mist of the fluid and can thus be lubricated and/or cooled. This mist is created by oscillating components, such as pistons and connecting rods, such a mist no longer occurs in electric machines because there are no longer any oscillating components. Especially when the fluid is an oil, the mist is also referred to as oil mist. In reciprocating piston machines, the mist automatically, i.e., simply by its formation, leads to a sufficient supply and, in particular, wetting of the partners with the fluid. In contrast, in electric machines, the absence of oil mist means that a sufficient supply of fluid to the relevant locations cannot necessarily be guaranteed unless appropriate measures are taken, which are usually quite complex. An undersupply of fluid to a location can, for example, lead to undesirable heating of one of the previously mentioned elements, such as the radial shaft seal. This can then lead to excessive heating of the radial shaft seal and, as a result, to undesirable fluid leakage. An oversupply of the element, such as the radial shaft seal, with fluid is also disadvantageous. Such an oversupply can result in undesirable effects, such as undesirable foaming of the fluid and unfavorable pressure effects. For example, if the radial shaft seal is completely submerged in the fluid, the fluid could leak through the radial shaft seal, causing the fluid to undesirably flow from a wet side to a dry side or from a wet area to a dry area. While this may not be critical in an internal combustion engine, such a leak in an electrical machine can lead to undesirable effects such as leakage currents.

The invention now makes it possible to supply the location with a sufficient amount of fluid in a particularly simple manner, in particular in such a way that both an oversupply and an undersupply of the location with fluid can be avoided. The first rotational position and the second rotational position are respective positions of the cage, which assumes or can assume the respective position in the circumferential direction of the shaft and the cage relative to the outlet opening, running around the axis of rotation. If, for example, the shaft rotates about the axis of rotation relative to the component at a first speed different from zero, the cage rotates about the axis of rotation relative to the outlet opening and, for example, relative to the shaft at a second speed different from zero and different from the first speed, in particular by the cage being rotatable about the axis of rotation relative to the outlet opening and preferably also relative to the shaft. In particular, it is provided that the outlet opening can rotate with the shaft about the axis of rotation relative to the component, so that preferably the shaft and the outlet opening rotate about the axis of rotation relative to the component at the same first speed. Depending on the position of the cage, the outlet opening is open or closed, and thus more strongly released or more strongly blocked. Since the cage rotates at a different speed than the outlet opening about the axis of rotation relative to the component, so that the cage rotates or can rotate relative to the outlet opening, the outlet opening is periodically opened and closed, and thus periodically the outlet opening is more strongly blocked and more strongly released, so that, for example, within, in particular exactly, one complete rotation of the outlet opening or of the shaft, the cage is in the first rotational position for a first period of time and in the second rotational position for a second period of time. If, for example, the speed at which the outlet opening and thus, for example, the shaft rotates around the axis of rotation relative to the component increases, then although the ratio of the first time period to the second time period or of the first rotational position to the second rotational position per revolution does not change, due to the fluid inertia of the fluid, it can be assumed that there will be a lower total volume flow of the fluid flowing out of the outlet opening per unit of time. This means that at a high speed of the outlet opening or the shaft, the volume flow of the fluid flowing through the outlet opening and thus flowing out of the channel via the outlet opening is blocked or reduced compared to a lower speed of the outlet opening or the shaft. This can This can be advantageous in a system network because, for example, the aforementioned conveying device provides a particularly high, in particular maximum, flow rate of fluid at high speeds of the outlet opening or shaft, particularly due to consumer requirements such as cooling and/or lubrication of the electric machine. However, a resulting very large amount of fluid supplied to the location can be disadvantageous. The invention can prevent the location from being supplied with an excessive amount of fluid by blocking or reducing the volume flow at high speeds of the outlet opening or shaft compared to lower speeds. As a result, a sufficient amount of the fluid conveyed by the conveying device can be made available to other consumers. As a result, oversupply and undersupply of the location with fluid can be avoided, and it can be ensured that other consumers can be supplied with a sufficiently large amount of fluid.

In order to be able to avoid both a supply with an excessively large amount of fluid and a supply of the location with an unfavorably smaller amount of fluid in a particularly simple manner, one embodiment of the invention provides that the second sub-region opens the outlet opening more than the first sub-region and the first sub-region blocks the outlet opening more than the second sub-region in that the first sub-region is arranged closer to the outlet opening in the first rotational position, viewed outwards in the radial direction of the shaft, than the second sub-region in the second rotational position.

A further embodiment is characterized in that the outlet opening, through which the fluid (coolant and/or lubricant) can be discharged from the channel and thus guided to the area surrounding the channel, is formed in the shaft. This ensures an advantageous supply of the fluid to the location.

It has proven particularly advantageous if the rolling bearing has an inner bearing ring that is formed separately from the cage and separate from the shaft and preferably also separate from the rolling elements and is connected to the shaft in a rotationally fixed manner, which is also simply referred to as the inner ring. The outlet opening is arranged offset from the inner ring in the axial direction of the shaft, in particular completely, so that the fluid can be guided to the environment and thus to the point via the outlet opening, bypassing the inner ring. This means that the fluid bypasses the inner ring on its way from and out of the channel to or into the environment, i.e. does not flow through the inner ring. This can ensure an advantageous supply of the point with the fluid.

For example, the inner ring forms the aforementioned inner raceway for the rolling elements.

In order, for example, to be able to guide the fluid to the location in a particularly advantageous manner and to achieve a particularly advantageous supply of the location with the fluid, one embodiment of the invention provides that the outlet opening, through which the coolant and/or lubricant can be discharged from the channel and thus led to the area surrounding the channel, is formed in the inner bearing ring of the rolling bearing, which is formed separately from the cage and separately from the shaft and also preferably separately from the rolling elements and is connected to the shaft in a rotationally fixed manner, such that the aforementioned part of the channel runs as the first part in the shaft and a second part of the channel, arranged downstream of the first part, runs in the inner bearing ring. The second part is fluidically connected to the first part. Preferably, the second part directly adjoins the first part in the flow direction of the fluid flowing through the channel, such that no other, further part is arranged between the parts in the flow direction of the fluid flowing through the channel.

A second aspect of the invention relates to an electric machine for a motor vehicle. This means that the motor vehicle, also simply referred to as a vehicle and preferably designed as a motor vehicle, in particular as a passenger car, has the electric machine in its fully manufactured state and can be driven by the electric machine, in particular purely electrically. The electric machine has at least one bearing arrangement according to the first aspect of the invention. Advantages and advantageous embodiments of the first aspect of the invention are to be regarded as advantages and advantageous embodiments of the second aspect of the invention, and vice versa.

Preferably, the electrical machine is a high-voltage component whose electrical voltage, in particular electrical operating or nominal voltage, is preferably greater than 50 volts, in particular greater than 60 volts, and most preferably amounts to several hundred volts.

In order to be able to realize a particularly advantageous supply of the location with the fluid, it is provided in an embodiment of the second aspect of the invention that the electrical Machine having a stator and a rotor which is drivable by means of the stator and is thereby rotatable about the axis of rotation relative to the stator, wherein the rotor is arranged coaxially to the shaft.

In order to achieve a particularly advantageous supply of the fluid to the location, it has proven particularly advantageous if the shaft, which is in particular formed separately from the rotor, is connected to the rotor in a rotationally fixed manner.

As already described with regard to the first aspect of the invention, it is preferably provided that the outlet opening is rotatable with the shaft about the axis of rotation relative to the component, so that preferably the shaft and the outlet opening are rotatable at the same speed about the axis of rotation relative to the component and, for example, also relative to the cage.

In a further embodiment of the second aspect of the invention, the electric machine comprises a housing that directly defines a receiving space. The stator is accommodated in the receiving space. For example, the stator is formed separately from the housing and is connected to the housing in a rotationally fixed manner. The component is preferably a housing part of the housing. This ensures an advantageous supply of fluid to the location.

A third aspect of the invention relates to a motor vehicle, also simply referred to as a vehicle, and preferably designed as a motor vehicle, in particular as a passenger car, which has at least one electric machine according to the second aspect of the invention and can be driven, in particular purely electrically, by means of the electric machine. Advantages and advantageous embodiments of the first aspect and the second aspect of the invention are to be regarded as advantages and advantageous embodiments of the third aspect of the invention, and vice versa.

• 1 ausschnittsweise eine schematische und perspektivische Schnittansicht einer elektrischen Maschine eines Kraftfahrzeugs;
• 2 ausschnittsweise eine schematische und geschnittene Perspektivansicht einer ersten Ausführungsform einer Lagerungsanordnung der elektrischen Maschine;
• 3 ausschnittsweise eine schematische und teilweise geschnittene Perspektivansicht der Lagerungsanordnung gemäß der ersten Ausführungsform;
• 4 eine schematische Perspektivansicht eines Käfigs eines Wälzlagers der Lagerungsanordnung;
• 5 eine schematische Vorderansicht des Käfigs;
• 6 ausschnittsweise eine schematische und geschnittene Perspektivansicht des Käfigs; und
• 7 ausschnittsweise eine schematische und teilweise geschnittene Perspektivansicht einer zweiten Ausführungsform der Lagerungsanordnung.

Further details of the invention will become apparent from the following description of preferred embodiments with the accompanying drawings. In the drawings:

• 1 a partial schematic and perspective sectional view of an electrical machine of a motor vehicle;
• 2 a partial schematic and sectional perspective view of a first embodiment of a bearing arrangement of the electrical machine;
• 3 a partial schematic and partially sectioned perspective view of the bearing arrangement according to the first embodiment;
• 4 a schematic perspective view of a cage of a rolling bearing of the bearing arrangement;
• 5 a schematic front view of the cage;
• 6 a partial schematic and sectional perspective view of the cage; and
• 7 a schematic and partially sectioned perspective view of a second embodiment of the bearing arrangement.

In the figures, identical or functionally identical elements are provided with the same reference symbols.

1 shows a detail in a schematic and sectional perspective view of an electric machine 1 of a motor vehicle, also referred to simply as a vehicle, which can be driven by means of the electric machine 1, in particular purely electrically. The electric machine 1 has a 1 particularly schematically shown stator 2 and one in 1 partially visible rotor 3, which is driven by means of the stator 2 and is thereby rotatable about a rotational axis 4 relative to the stator 2. Furthermore, the electric machine 1 has a separate from the stator 2 and separate from the rotor 3 and additionally provided in 1 a particularly schematically illustrated housing 5 which delimits, in particular directly, a receiving space 6. The stator 2 is formed separately from the housing 5 and is arranged in the receiving space 6 and is connected to the housing 5 at least in a rotationally fixed manner, such that relative rotations between the stator 2 and the housing 5 about the axis of rotation are prevented. The rotor 3 is rotatable about the axis of rotation 4 relative to the housing 5 and is at least partially arranged in the receiving space 6. Furthermore, the electric machine 1 has a shaft 7 which is at least partially arranged in the receiving space 6. The shaft 7 is formed separately from the rotor 3 and is connected to the rotor 3 in a rotationally fixed manner, such that the shaft 7 is rotatable about the axis of rotation 4 relative to the stator 2 and relative to the housing 5. The shaft 7 is formed separately from the rotor 3, separately from the stator 2 and separately from the housing 5. The housing 5 has a housing part 8, by which the receiving space 6 is at least partially and directly delimited. Thus, the shaft 7 is rotatable about the rotational axis 4 relative to the housing part 8. It can be seen that the housing part 8 is a component of the electrical machine 1, wherein the component is formed separately from the shaft 7. and is provided in addition to the shaft 7. In the present case, the component (housing part 8) is also formed separately from the stator 2 and is connected at least indirectly, in particular directly, to the stator 2, in particular in such a way that relative rotations between the housing part and the stator 2 about the rotation axis 4 are prevented.

The electrical machine 1 has a bearing arrangement 9 in which the shaft 7 is rotatably mounted on the housing part 8 about the rotation axis 4 relative to the housing part 8 via at least one rolling bearing 10.

Out of 2 It can be seen that the rolling bearing 10 has a bearing inner ring 11, also simply referred to as the inner ring, and a bearing outer ring 12, also simply referred to as the outer ring. The bearing inner ring 11 is formed separately from the shaft 7 and separately from the rotor 3 and is connected to the shaft 7 in a rotationally fixed manner, in particular bypassing the rotor 3. The bearing outer ring 12 is formed separately from the housing 5 and thus separately from the housing part 8, and is connected to the housing part 8 and thus to the housing 5 in a rotationally fixed manner. The bearing inner ring 11 and the bearing outer ring 12 are formed separately from one another. Since the bearing inner ring 11 is connected to the shaft 7 in a rotationally fixed manner, the bearing inner ring 11 can rotate about the axis of rotation 4 with the shaft 7 relative to the bearing outer ring 12. It can thus be seen that the shaft 7 and the bearing inner ring 11 are rotatable about the axis of rotation 4 relative to the bearing outer ring 12 and relative to the housing part 8 and relative to the housing 5. The rolling bearing 10 also has a cage 13, also referred to as a bearing cage or rolling bearing cage, which is formed separately from the shaft 7, separately from the bearing inner ring 11 and separately from the bearing outer ring 12 and also separately from the rotor 3 and separately from the stator 2 and separately from the housing 5. In addition, the rolling bearing 10 has rolling elements 14 which are arranged successively in the circumferential direction of the shaft 7 and in the circumferential direction of the cage 13. The circumferential direction of the shaft 7 coincides with the circumferential direction of the cage 13 and vice versa, wherein the respective circumferential direction runs around the axis of rotation 4. The respective circumferential direction is illustrated by a double arrow 15. 2 and 3 show a first embodiment of the bearing arrangement 9. 7 shows a second embodiment of the bearing arrangement 9. In the first embodiment and in the second embodiment, the respective rolling element 14 is designed as a respective ball. By means of the cage 13, the rolling elements 14 are designed as a respective ball. By means of the cage 13, the rolling elements 14 are held at a distance from one another in the circumferential direction of the shaft 7 and thus of the cage 13, in particular when viewed in pairs. The bearing inner ring 11 forms a first, inner raceway L1 for the rolling elements 14, and the bearing outer ring 12 forms an outer, second raceway L2 for the rolling elements 14. If the shaft 7 and thus the bearing inner ring 11 rotate about the axis of rotation 4 relative to the housing part 8 and thus relative to the bearing outer ring 12, the rolling elements 14 roll, in particular directly, on the raceways L1 and L2. In particular, the cage 13 is rotatable about the rotation axis 4 relative to the shaft 7 and thus relative to the bearing inner ring 11. Furthermore, it is conceivable that the cage 13 is rotatable about the rotation axis 4 relative to the housing part 8 and thus relative to the bearing outer ring 12. The bearing inner ring 11 and the bearing outer ring 12 are collectively referred to as bearing rings.

Cage 13 is particularly well made 4 , 5 and 6 can be seen, from which the rolling elements 14 are also clearly visible. For example, a respective receiving opening of the cage 13 is assigned to the respective rolling element 14, wherein the respective receiving opening is preferably designed as a respective through-opening which is continuous, for example, in the radial direction of the shaft 7 and thus of the cage 13. The radial direction of the shaft 7, whose axial direction runs perpendicular to the radial direction of the shaft 7, coincides with the axis of rotation 4, so that the radial direction of the shaft 7 runs perpendicular to the axis of rotation 4. For example, the respective rolling element 14 penetrates the respective receiving opening of the cage 13 assigned to the respective rolling element 14, in particular in the radial direction of the shaft 7.

The bearing arrangement 9 and thus the electric machine 1 also have a channel 16 that runs at least partially in the shaft 7. In the first embodiment, the channel 16 runs partially in the shaft 7 and partially in the bearing inner ring 11, which is formed separately from the shaft 7 and connected to the shaft 7 in a rotationally fixed manner, so that in the first embodiment, a first part T1 of the channel 16 runs in the shaft 7 and a second part T2 of the channel 16 runs in the bearing inner ring 11. The parts T1 and T2 are fluidically connected to one another and adjoin one another directly, i.e. immediately, in such a way that the second part T2 is arranged downstream of the part T1 in the flow direction of a coolant and/or lubricant flowing through the channel 16. This means that the coolant and/or lubricant flows during operation of the electrical machine in the said flow direction through the channel 16 and thus through the parts T1 and T2, such that the part T2 is arranged downstream of the part T1 in the flow direction of the coolant and/or lubricant flowing through the channel 16, wherein Part T2 is directly connected to part T1 in the flow direction of the coolant and/or lubricant flowing through channel 16. Thus, no other, further part of channel 16 is arranged between parts T1 and T2. The coolant and/or lubricant is also simply referred to as a fluid and is preferably a liquid, in particular an oil. The fluid is most preferably a component of the electrical machine 1. The channel 16 and thus parts T1 and T2 can be flowed through by the fluid. 1 It can be seen that the channel 16, in particular precisely, has an outlet opening 17 through which the fluid can flow, via which the fluid can be discharged from the channel 16 in order to thereby supply at least one cooling and/or lubricating point, also referred to simply as a point, with the cooling and/or lubricating agent (fluid). The cooling and/or lubricating point is in 1 recognizable and marked with S. Recognizable from 1 is also an element designed as a sealing element 18, which is designed separately from the housing part 8 and separately from the shaft 7 and is held on the housing part 8 in such a way that relative rotations about the axis of rotation 4 between the housing part 8 and the sealing element 18 are prevented. The shaft 7 is therefore rotatable about the axis of rotation 4 relative to the sealing element 18. The sealing element 18, also referred to as a sealing element, is in this case a radial shaft sealing ring, the sealing lip 19 of which directly contacts an outer circumferential surface 20 of the shaft 7. If the shaft 7 rotates about the axis of rotation 4 relative to the housing part 8 and relative to the sealing element 18, the sealing lip 19 and thus the sealing element 18 slide directly on the outer circumferential surface 20 and thus on the shaft 7. By means of the sealing element 18, the shaft 7 is sealed against the housing part 8, whereby, for example, a so-called dry space 21 of the electrical machine is sealed in the axial direction of the shaft 7 against a so-called wet space 22 of the electrical machine 1. For example, the dry space 21 and the wet space 22 are respective subregions of the receiving space 6. By means of the sealing element 18, an excessive amount of fluid is thus prevented from overflowing from the wet space 22 into the dry space 21. In particular, it can be seen that the outlet opening 17 is arranged in the wet space 22, so that the channel 16 opens into the wet space 22 via the outlet opening 17, in particular bypassing the dry space 21. The wet space 22 is thus an environment or a component of an environment of the channel 16 and the shaft 7.

Recognizable from 2 is that the outlet opening 17 is at least partially, in particular at least predominantly and thus at least more than half or completely, overlapped by the cage 13 towards the outside in the radial direction of the shaft 7. The cage 13 is rotatable relative to the outlet opening 17 and relative to the shaft 7 about the axis of rotation 4. For example, the cage 13 is formed from a plastic. For example, the outlet opening 17 is designed as a bore and thus formed by machining. It is conceivable that the part T1 and/or the part T2 is designed as a respective bore and thus produced by machining.

In order to be able to realize a particularly advantageous supply of the fluid to the point S, at which the sealing lip 19 directly touches the shaft 7, in particular in such a way that both an oversupply of the fluid to the point S and an undersupply or insufficient supply of the fluid to the point S can be avoided, it is provided in the bearing arrangement 9 that the cage 13 has at least two sub-regions that are directly consecutive in the circumferential direction of the cage 13 and the shaft 7 running around the axis of rotation 4 and each extend in the circumferential direction of the cage 13, namely a first sub-region TB1 and a second sub-region TB2. Due to the fact that the cage 13 is rotatable about the axis of rotation 4 relative to the outlet opening 17, the cage 13 is rotatable about the axis of rotation 4 relative to the outlet opening 17 and also relative to the shaft 7 into at least or exactly two different rotational positions, namely a first rotational position D1 ( 3 ) and a second rotational position D2 ( 2 ). Recognizable from 2 and 3 is that in the first rotational position D1 of the cage 13, the outlet opening 17 is at least partially, in particular at least predominantly and thus at least more than half or completely, overlapped by the first partial region TB1 in the radial direction of the shaft 7 towards the outside. In the second rotational position D2 of the cage 13, the outlet opening 17 is at least partially, in particular at least predominantly and thus at least more than half or completely, overlapped by the second partial region TB2 in the radial direction of the shaft 7 towards the outside. In the present case, in the first rotational position D1, the outlet opening 17 is arranged in the radial direction of the shaft 7 towards the outside, in particular completely, without overlapping with the partial region TB2, and in the second rotational position D2, the outlet opening 17 is arranged in the radial direction of the shaft 7 towards the outside, in particular completely, without overlapping with the first partial region TB1.

In the second rotational position D2, the second partial area TB2 opens the outlet opening 17 in the radial direction of the shaft 7 to a greater extent than the first partial area TB1 in the first rotational position D1. Conversely, in the first rotational position D1, the first partial area TB1 blocks the outlet opening 17 in the radial direction of the shaft 7 to a greater extent than the second partial area TB2 in the second rotational position D2. This is such that realized that the first sub-area TB1 in the first rotational position D1 is arranged closer to the outlet opening 17 in the radial direction of the shaft 7 than the second sub-area TB2 in the second rotational position D2. Conversely, the second sub-area TB2 in the second rotational position D2 is arranged further away from the outlet opening 17 in the radial direction of the shaft 7, viewed outwards, than the first sub-area TB1 in the first rotational position D1. As a result, in the first rotational position D1, the fluid flowing through the outlet opening 17 and thus flowing out of the channel 16 via the outlet opening 17 is throttled more strongly by means of the first sub-area TB1 than in the second rotational position D2 by means of the second sub-area TB2. As a result, both an insufficient supply of the point S with the fluid and an oversupply of the point S with the fluid can be avoided both at lower speeds of rotation of the shaft 7 and at higher speeds of rotation of the shaft 7.

At the 2 and 3 In the first embodiment shown, the outlet opening 17 is formed, in particular completely, in the bearing inner ring 11, so that the part T2 and thus the channel 16 as a whole, viewed in the flow direction of the fluid flowing through the channel 16, ends at the outlet opening 17. The fluid thus flows out of the channel 16 via the bearing inner ring 11.

At the 7 In the second embodiment shown, the outlet opening 17 is formed, in particular completely, in the shaft 7 and is arranged offset in the axial direction of the shaft 7, in particular completely, relative to the bearing inner ring 11, so that the fluid flows out of the channel 16 via the outlet opening 17, bypassing the bearing inner ring 11.

The sub-regions TB1 and TB2 of the cage 13 are segments of the cage 13, with the sub-region TB1 being referred to as the first segment and the sub-region TB2 as the second segment of the cage 13. In the first rotational position D1, the outlet opening 17 is located below the first segment, and in the second rotational position D2, the outlet opening 17 is located below the second segment. The segments block the outlet opening 17 to different degrees, so that the segments throttle the fluid flowing through the outlet opening 17 and thus out of the channel 16 via the outlet opening 17 to different degrees, thus preventing it from flowing through the outlet opening 17 and thus out of the channel 16 via the outlet opening 17 to different degrees. As a result, it is possible to supply the point S with the fluid in a particularly simple manner in such a way that both a supply of the point S with an excessively large amount of the fluid and a supply of the point S with an unfavorably small amount of the fluid can be avoided.

Recognizable from 1 is that the shaft 7 is arranged coaxially with the rotor 3. Furthermore, the shaft 7, which is formed separately from the rotor 3, is connected to the rotor 3 in a rotationally fixed manner. Via the shaft 7, the electric machine 1 can provide drive torques for driving the motor vehicle, in particular purely electrically.

Out of 2 and 3 it can be seen that the outlet opening 17 is formed and thus arranged in a groove 23, wherein in the first embodiment the groove 23 is a groove in the bearing inner ring 11. The groove 23 is delimited, in particular directly delimited, on both sides in the axial direction of the shaft 7 by respective first wall regions, in this case the bearing inner ring 11, and in the radial direction inwards of the shaft 7 the groove 23 is delimited, in particular directly, by a second wall region, in this case the bearing inner ring 11. The wall regions are respective solid bodies. It can also be seen that the first partial region TB1 engages in the groove 23. In the present case, it is provided that there is no contact between the first partial region TB1 and the bearing inner ring 11 and there is also no contact between the partial region TB2 and the bearing inner ring 11. For example, during operation of the electrical machine 1, a film formed by the fluid forms in the groove 23, which film is also referred to as an oil film, particularly when the fluid is in the form of an oil. If the cage 13 rotates about the axis of rotation 4 relative to the bearing inner ring 11 and in particular the shaft 7, the cage 13 slides, for example, on the said film. The axial direction of the shaft 7 is illustrated by a double arrow 24 and coincides with the axis of rotation 4. The radial direction of the shaft 7 and thus of the cage 13 is illustrated by a double arrow 25 and runs perpendicular to the axial direction of the shaft 7 and the cage 13. The cage 13 and the rolling elements 14 can be particularly well made of 4 and 5 can be recognized. Recognizable from 4 and 5 In particular, the cage 13 has a plurality of first sub-regions TB1 and a plurality of second sub-regions TB2, wherein the sub-regions TB1 and TB2 are arranged alternately one after the other in the circumferential direction of the cage 13 and the shaft 7 extending around the rotational axis 4. In particular, it is provided that a respective first number of the first sub-regions TB1 and a respective second number of the second sub-regions TB2 are equal. In the present case, a respective number is greater than 1, wherein the respective number is a positive integer.

In 6 a first extension of the respective first partial area TB1, running in particular in the circumferential direction of the cage 13, is defined by a first arrow P1, and in 6 A respective second extension of the respective second partial region TB2, extending in the circumferential direction of the cage 13, is illustrated by a second path P2. The respective extension defines, for example, a respective time period within a respective complete revolution of the shaft 7 and/or the cage, during which the outlet opening 17 is overlapped outwardly in the radial direction of the shaft 7, in particular without interruption, by the respective partial region TB1, TB2. In particular, the first extension and the second extension can differ from one another.

List of reference symbols

1

electric machine

2

stator

3

rotor

4

axis of rotation

5

Housing

6

recording room

7

Wave

8

Housing part

9

Storage arrangement

10

Rolling bearings

11

Bearing inner ring

12

Bearing outer ring

13

cage

14

Rolling elements

15

double arrow

16

channel

17

Exit opening

18

Sealing element

19

sealing lip

20

outer peripheral surface

21

Drying room

22

wet room

23

Nut

D1

first rotation position

D2

second rotation position

P1

first arrow

P2

second arrow

T1

first part

T2

second part

TB1

first sub-area

TB2

second sub-area

QUOTES CONTAINED IN THE DESCRIPTION

This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 10 2020 101 951 A1 [0002]

Claims (10)

Bearing arrangement (9) of a shaft (7) on a component (8) which is formed separately from the shaft (7) and provided in addition to the shaft (7), in which: - the shaft (7) is mounted on the component (8) via at least one rolling bearing (10) so as to be rotatable about an axis of rotation (4) relative to the component (8), - a channel (16) which runs at least partially in the shaft (7) and through which a coolant and/or lubricant can flow is provided, which channel has an outlet opening (17) through which the coolant and/or lubricant can flow, via which outlet opening the coolant and/or lubricant can be discharged from the channel (16) in order to thereby supply the at least one cooling and/or lubrication point (S) with the coolant and/or lubricant; and - the outlet opening (17) is at least partially overlapped outwards in the radial direction (25) of the shaft (7) by a cage (13) of the rolling bearing (10) which is rotatable about the axis of rotation (4) relative to the outlet opening (17) and relative to the shaft (7); characterized in that the cage (13) has at least two partial regions (TB1, TB2) which follow one another in the circumferential direction (15) of the cage (13) and each extend in the circumferential direction (15) of the cage (13), namely: - a first partial region (TB1) by which the outlet opening (17) is at least partially overlapped outwards in the radial direction (25) of the shaft (7) in at least one first rotational position (D1) of the cage (13); and - a second partial region (TB2) by which, in at least one second rotational position (D2) of the cage (13), the outlet opening (17) is at least partially overlapped outwards in the radial direction (25) of the shaft (7), wherein the second partial region (TB2) opens the outlet opening (17) to a greater extent than the first partial region (TB1), which blocks the outlet opening (17) to a greater extent than the second partial region (TB2). Storage arrangement (9) according to Claim 1 , characterized in that the second partial area (TB2) opens the outlet opening (17) to a greater extent than the first partial area (TB1) and the first partial area (TB1) blocks the outlet opening (17) to a greater extent than the second partial area (TB2) in that the first partial area (TB1) in the first rotational position (D1) is arranged closer to the outlet opening (17) in the radial direction (25) of the shaft (7) than the second partial area (TB2) in the second rotational position (D2). Storage arrangement (9) according to Claim 1 or 2 , characterized in that the outlet opening (17), via which the coolant and/or lubricant can be discharged from the channel (16) and thereby guided to an environment (22) of the channel (16), is formed in the shaft (7). Storage arrangement (9) according to Claim 3 , characterized in that the rolling bearing (10) has a bearing inner ring (11) which is formed separately from the cage (13) and separately from the shaft (7) and is connected to the shaft (7) in a rotationally fixed manner, wherein the outlet opening (17) is arranged offset from the bearing inner ring (11) in the axial direction (24) of the shaft (7). Storage arrangement (9) according to Claim 1 or 2 , characterized in that the outlet opening (17), via which the coolant and/or lubricant can be discharged from the channel (16) and thereby guided to an environment (22) of the channel (16), is formed in a bearing inner ring (11) of the rolling bearing (10) which is formed separately from the cage (13) and separately from the shaft (7) and is connected to the shaft (7) in a rotationally fixed manner, so that a first part (T1) of the channel (16) runs in the shaft (7) and a second part (T2) of the channel (16), arranged downstream of the first part (T1), runs in the bearing inner ring (11). Electrical machine (1) for a motor vehicle, with at least one bearing arrangement (9) according to one of the preceding claims. Electrical machine (1) according to Claim 6 , characterized in that the electrical machine (1) has a stator (2) and a rotor (3) which can be driven by means of the stator (2) and is thereby rotatable about the axis of rotation (4) relative to the stator (2), wherein the rotor (3) is arranged coaxially to the shaft (4). Electrical machine (1) according to Claim 7 , characterized in that the shaft (7) is connected to the rotor (3) in a rotationally fixed manner. Electrical machine (1) according to one of the Claims 6 until 8 , characterized by a housing (5) directly delimiting a receiving space (6), wherein the stator (2) is received in the receiving space (6), and wherein the component (8) is a housing part (8) of the housing (5). Motor vehicle, with at least one electrical machine (1) according to one of the Claims 6 until 9 .